Hydraulic transmission gear



May 3,1938. H. www@ 2,116,461

HYDRAULIC TRANSMISSION GEAR Filed April 4. 1934 l' Patented May 3 1938 UNITED STATES PATENT OFFICE HYDRAULIC TRANSMISSIGN GEAR Hermann Wittingen', Berlin-Wilmersdorf,

Germany Application April 4, 1934, sensi No. 'nanos L 1n sammy April o. ma p s emma (ci. ca -54) In the well-known hydraulic'transmission gears or turbo-transformers which consist -of pump wheels. turbine wheels and guide wheels the speed of the turbine wheels, viz. the secondary wheels.

5 changes within wide limits in accordance with the resistance to be overcome. pump wheels being kept constant, the nor'mal and the highest efficiency will be obtained with `a deiimte torque of the turbine, viz. the socalled norma torque of the turbine wheels.

When the 'f stance at su. 'ing or by hard braking, the torque oi' the turbine increases by itself and the amount of increase will ne dependent on the number, the radii and the blading of the turbine wheels and the guide apparatus as well as of the type ofthe pump. As the speed of the turbine increases, the

torque inversely decreases until in the case of no-load work the torque has dropped to aero. when hydraulic transmissions are built in, e. g. into automobiles. various tractive efforts, that is various torques mustbe successively overcome. Consequently the speed of the turbine adjusts itself according to the torque to be overcome and thus also the running speed of the car is automatically adapted without steps to the amount attainable. Therefore the decrease of the speed is automatically accompanied by an increase of the torque.

p The hydraulic transmission gears hitherto built were as a rule intended forships and similar purposes where an increase of torque for starting would be unnecessary and useless. The only intention was to arrive at a maximum emciency with the normal run. Of coursefalso in this instance a corresponding increase of the torque took place at starting, viz. with theminimum of angular speed, and in such a way that the starting torque amounted to about double the normal torque and the no-load speed to about double the normal speed of the turbine. The curve of the emciency was similar to a parabola the vertex of which coincides with the point of normal speed. .gg `In the case of land vehicles, lifting machinery etc. it is desirable that the tractive effort. viz. the torque be increased at starting as muchas possible by a suitable design 'of the hydraulic system. The ideal shape of the speed curve would be the however, could be arrived at only in the case oi gears free of lossv and would result at an infinitely large tractive effort in the sta-rt. f The ideal tractive-eifort hyperbolel can, of course, not 'be gg attained in a transmission gear practically built,

The speed of the d of the turbine is reduced, for in- 1. so-called ideal tractive-eiort hyperbole," which,

although it would be the most ideal design for. the use on land vehicles etc. l

Now, it is an object of the present invention to provide for a hydraulic transmission gear which is particularly suited for land' vehicles, lifting machinery andthe like and shows a torque or tractive edort curve as favorable as possible, that is a torque curve which -lies between the ideal tractive-effort parabola and the `straight-line increase of torque actually prevailing in"- the hylo draulic transmission gears already known.

The novel means found out for the solution of this problem and further improvements of the hydraulic transmission gear as detailedly specified in the following description are the subject u matter of the present invention. The accompanying drawing shows several embodiments of the invention, and in them A Figpl is a chart of the dependencies prevaillng between torque, speed and efficiency in prior transmissiongears, this chart explaining the object of the present invention.

Fig. 21s a further chart and shows the circumferential velocity at the outlet of the turbine as plotted against .the relative discharge velocity and 25 the outlet angle.

Fig. 3 is a partiallsection through a hydraulic transmission gearf according to the invention.

Fig. 4 is a partial section through Fig. 3 accord ing tothe line IV-IV and seen in the direction so of the arrows. c

Fig. 5 shows the right Apart of Fig. Sand illustrates another embodiment of the guide blades,

. and r,

f Fig. 6 is a section through Fig. 5 according to 35 the line VI-VI seen in the direction ofthe arrows.. ,g

In the chart, Fig. 1, the abscissae represent the angular speeds and the 'ordinates the torques.

With a normal speed num-m the normal torque is 40 Mn. When the speed is decreased. the torque increases; when, however, the speed rises, the' torque drops. l

In the well-known earlier constructions of the yinventor the latter used turbines with an g5 sion directed to the interior (Francis type) with three to ve turbinestages or there were used two or three complete turbine circuits with the same direction of rotation. -This arrangement resulted in torque curve M designated by l2 in so Fig. l, viz. infa straight line. At the start the .torque was about double as high as the normal torque Mn and when running without load the speed m. was about double as high as .the normal Speed. v ss' Another well-known transmission gear (the Rieseler gear U. B. Patent No. 1,727,903) has a torque line designated by III in Fig. 1, when running in the hydraulic circuit with a two-stage turbine and a guide device alternately immobilized by hard braking or running free. In this instance the starting torque is evenlower so that this arrangement is still less suitable for land vehicles, lifting machinery etc. Y

In the other transmission gears known, for instance the Lysholm-Ljungstrm gears (U. S. Patent No. 1,900,120) a great many turbine steps, but at least three stages with radial blading are used and particularly steep outlet angles are provided for. Also in that instance the intention was to fully remove the tangential component cu of the absolute velocity of flow prior to the return of the water into the pump (so-called vertical admission). 'I'his resulted in a curve like that designated by II in Fig. 1 and which is much more advantageous than curve I. It lies between the latter and the dotted ideal tractive-effort hyperbola as plotted in Fig. 1 which also comprises the parabolic curve of the emciency 7.

In order to obtain torques similar to those represented by curve II, Coats (U. S. Patent 1,760,397) further made use of a guide apparatus which comprised one fixed guide blade rimand four movable guide blade rims, which are either allowed to freely revolve or the blades of which can freely turn. This turbine was of the Francis tylle with a small inlet radius and a large outlet r us. v

It is obvious lfrom this that as far as it was possible to arrive at a torque curve lying between the straight torque line I and the. ideal hyperbola, it was necessary to make use ofvery intricate designs.

Now, the inventor has found out that degrees of increase oi' the tractive eilort, viz. torque curves like those shown by II and which were attained, so-far, only with at least three turbine stages (six wheels) or with one ilxed and four revoluble guide blade rims (seven wheels), can already be arrived at with one single turbine stage in one circuit comprising three fixed wheels, accordingly with a fraction oi' the 'means' hitherto necessary for that purpose. f

This effect absolutely unexpected and diametrically opposed to the notion of other specialists is, according to the invention, substantially obtained by the essential combination oi' the following features, namely:

(a) In the cycle there is disposed in combination with a pump wheel only the .one secondary wheel the inlet radius of which does not exceed the'outlet radius (consequently no Francis turbines).

(b) Ihe blades of the secondary wheel form nat angles with the circumference at the outlet whereby the peripheral velocity u at the outlet of the turbine must be of the magnitude of the relative discharge velocity w at this point which results in the outlet angles being smaller than 35 degrees (Fig. 2).

(c) The blades of the secondary wheel must be substantially thickened at the inlet and eventually rounded'oil'. y

(d) 'I'he guide means or/and the secondary wheel consist of two rims one of which carries blades continually operative while the.other rim carries supplementary blades used for slow angular speeds and which at higher angular speed are withdrawn from action. The totality of these features results in the surprising progress here disclosed.

. speed varying between nor The addition hitherto usual of centripetal turbines of the Francis type (inlet radius larger than outlet radius) to the pump vwhich works here with very variable delivery heads (and lquantities of water) sensibly impairs e. g. the increase of torque of turbines showingthe features (a) or (b)+(c). l

The great increase'of the momentum intended by` the invention cannot be attained with gears having steep blade angles or blades insuiliciently thickened.

The substantially thickened blade heads, per se known in water turbines, serve here the special purpose of sumciently safely providing for the highly increased torque (particularly during the start) by means oi' preferably one single turbine rim, in a way which is satisfactory hy draulically and with respect to mechanical strength. whereas this torque was distributed over 2 or 3l turbine rims in the earlier types (U. S. P'atent 1,900,120). f

The invention is further based on the following important ilndingz`0ccasionally it had been observed'on the old Fourneyron turbines (outlet radius larger than inlet radius) that the torque characteristic was slightly curved upward towards the hard-braking point (see Escher-Dubs Die 'I'heorie der Wasserturbinen, 3rd edition, page 2 and pages 171-174). These. turbines built into rivers, however, work under other hydraulic conditions than the present transmission gears (torque transformers) In s ite of the angular al and zero the height of fall of the river remains constant. In the selfcontained transmission gear, however, not only the. head oi' the turbine but also the quantity of Water change sensibly, since in the short-circuited circuit a reaction directly takes place on the pump which does not furnish any constanthead of water but a head which`very sensibly'varies with the quantity of Water delivered (cf. the Q-H characteristic). The quantity of water, however, adjusts itself in such a Way that the total vresistances in the pump, turbine and uti- which is advantageous for .the maximum ei'- ficiency, is also superior i'or the spontaneous increase of the tractive effort in the start.

Fig. 2 shows one of the usual turbine triangles in which accordingy to the invention the circumferential velocity u and the velocity of flow (here the relative velocity at the channel outlet) 'are of about the vsame magnitude. In the case of hard braking w is sensibly increased. The blade angles z are then smaller than 35 degrees, while in the case of larger angles unsatisfactory ratios u/w would be the result (viz. too small u as compared with w). The blade may e. g. have the rounded shape shown which is per se knownin steam turbines, propellers, pumps and water turbines, it may, however, also be pointed in a suitable manner but at any rate it must have substantially thickened .inlet ends.

In the embodiment shown by Fig. 3 the primary 75 s,1ic,4e1 i 3 i anaft 1 carries the pump wheel 2, which delivers the-water int'o thecoaxial turbine or secondary wheel 3l, 30, which is coupled with the secondary shaft 9 by lmeans of the disc i. From here the -water flows through a bladeless channel I9 to the guide rims 3i, Il' disposed opposite tothe secondary wheel and finally back through the bladeless chamber 40 into the pump. v

The guide rim 3|. is supported by a carrier 36 10 which can. as desired, rotate on or with the primary shaft I or may beimmobilized against rotating by the brake 38.

At the maximum speed the guidedevice may be freed by a release' of the hard braking at 38 so that the circuit is converted into a soft hydraulic clutch. At the maximum running speed the latter may even be replaced by a Vrigid coupling consisting in s tooth ofiriction clutch 35 so that the eiiiciency 1, is raised to practically 100% and 2c all means :today available for the increase of tractive effort and eiilciency are combined within a minimum of space.

For increasing the tractive effort and at the same time the emciency the guide device con- .25 sista of two rims iti, 3i .the one oi which 3i being adapted to be inserted into the circuit or withdrawn into the. chamber t2 according to the speed desired in an axial direction into the same circuit. f

3@ According to the invention, this measure can be further improved by not only a second guide apparatus but also a cond turbine wheel all' beinglinserted in'a suita le way, e.v g. also by an axial displacement into and from the chamber 3d.

35 Then a turbine wheel adapted to the particular running speed will correspond' to each guide'apparatus (Fig. 3i.

f In some instances this-will, however, present the disadvantage that the mechanical connection ,mbetweenthe casing E and the core 33 of the circuit or other corresponding members is lost so .that special supporting blades leaving the twist substantially unchanged must be used in order to reestablish this connection.

' 45 This inconvenience by itself not essential can be overcome according to the invention by the particular guide blades of the-guide device and/or vthe blades of the turbine being each divided into Y an inlet and an outlet part the vlatter of which y '50 is continually used and at bthe same time connects the outside wall i and the internal core Il oi the circuit with one another while the inlet -part is so shaped that it completes the outlet part suited for high and medium speeds only, to a kind 55.01' hookgt blade which is on the contrary adapted I to low speeds and particularly to the development of maximum tractive' eiorts .for starting., By this arrangement the double or multiple branched circuits for transmission gears as disclosed by '60 earlier patentsof the inventor are so to speak combined into s. single circuit sothat an essential simplification and'improvement ci the set is obtained, the Amore so as it was found 'out thatI the pump in any instance common to the latter can 55 show. deilnite properties which are hydraulically advantageous for either speed.

' Fig. 4 shows such special blades consisting each of an inlet part Il' and an outlet part 3l and which are suited for the change both of the guide 70" device and of the turbine impellers..l 3| e. g. has` the typical shape of the reaction blades correspondingt high and medium speeds of the turbinewhile the combination, oi Il' and 3| results in an advantageous laction or impuke turbine.

75 bladins.

i In Fig. 3 3| is the rim continually used in the guide device whilei' is the supplementary rim lo which is adapted to disappear in the chamber l2 connected with the stationary guide device. Ihe 'displacement is e. g. accomplished in the wellknown way by the hydraulic pressure in the gear itself as illustrated and described in the inven- 15 tor's Patent 1,199,361. This feature is longv known and therefore not a subject matter oi the present invention. The supplementary rim 3i is naturally disposed in the direction of flow in iront ofthe outlet rim 3i continuously used, viz. an in the present instance at a larger radius than 3i.

In the sarne way the turbine outlet rim malr also, for the development ofthe maximum starting tractive efforts and efiiciencies, be rigidly cornI nected with the casing 5 and the core 33 while in 25 the case of medium andhigh running speeds the supplementary rim til can disappear' into the chamber 3d of the secondary runner. The rimreceiving chambers 32 and tt may be disposed as. desired either within the core -or on the outau side of the casing.

A further advantage of vthe invention consists in that, if desired, it is possible to obtain an additional braking effect by means of the hy draulic gears. This eifect is particularly desir- 35 able in the case of long descents or when the driver encounters an unexpected osbtruction so that braking with any possible means imposes itself. Afterhaving reached a certain speed the hydraulic gear willas a rule be used'as a `couiso pling or the driver will have the car to run with a direct mechanical clutch engagement so that according the above statement it would be neces- Saly to render the guide device inoperative in the circuit either by vfree running or by a withdrawal frorrrthe circuit.

When now with such 'a speed the secondary shaftis to be braked, the guide wheel is inserted again' by being immobilized or returned into the circuit. In the lsameway in which initially a sensible increase of the torque was obtained in the start, the guide device being inserted, viz. the transition from the coupling to the torque transforming effect, will result in a powerfulv braking action on the secondary part. A par- 55 ticuiarly powerful `braking effect is obtained by the primary shaft, for'instance the engine, being braked to stoppage. In either instancethe hydraulic gear acts as,a water brake. The essential features of the invention 'as 60 characterized in the claims are naturally appliable independently of any particular features described land the embodiments shown by the drawing are also readily appliable to embodiments of turbines, pumps and hydraulic trans-i .65 mission gears in g. general way.

I claim:

1. A hydraulic transmission gear for an inten-V slied automatic torque increaseat the .'stox't. comprising aprimary pump wheel, only one secondary wheel the inlet radius of which does not lexceed the outlet radius, andthe .blades Yof which, substantially thickened at'the inlet. and eventually rounded ofi, andl formed with` dat angles, with the circumference at the outlet 'II whereby the relative discharge velocity (ws) and the peripheral velocity (us) at that point are of substantially the same magnitude at the normal angular speed of maximal eiiiciency (nam), a chamber connecting the outlet of the secondary wheel with the inlet oi the pump wheel, guide l means operable in said chamber and consisting of ler tive discharge lvelocity (wz) and the peripheral velocity (ua) at that point are oi' substantially the same magnitude at thenormal angular speed of maximal eiiiciency -(mmm). a chamber connecting the outlet oi the secondary wheel with the inlet oi the pump wheel, guide means operable inv said chamber and consisting of two rims. the secondary wheel one of which carries blades continually operative while the other rim carries supplementary blades operative 'for slow angular speeds of the secondary wheel, and means for withdrawing the supplementary blades from action at higher angular speeds.

3.* A hydraulic transmission gear according to claim 1, in which also the secondary wheel consist of two rims, one of which carries blades continually operative while the other rim carries supplementary blades for slow angular speeds of the secondary wheel and which at higher angular speeds are withdrawn from action by axial displacement.

4.- A hydraulic transmission gear according toclaim 1 in which the supplementary blades being so arranged as to overlap the thickened heads ot the continually operative blades.

5. A hydraulic transmission gear for an intensiiied automatic torquev increase atjthe start,

comprising a primary. pump wheel, a secondary ,fwheel, the inlet radius of which does not exceed the outlet radius, and the blades of which.

substantially thickened at the inlet and eventu-f.

rims oneoi' which carries guide blades continually operative while thel other rim carries supplementary blades for slow angular speeds of the secondary wheel and means for rendering the supplementary blades inoperative at higher angular speeds and the guide means being arranged on the side of the circuit opposite to the side ot the secondary wheel. f'

6. A hydraulic transmission gear for an inten-l -siiled automatic torque increase at the start, comprising a primary pump wheel, a secondary wheel, the inlet radius of which does not exceed the outlet radius, and the blades oi' which, substantially thickened at the inlet and eventually rounded oir, iorm'ilat angles s: with the circumference at the outlet whereby the relative discharge velocity (wz) and the peripheral velocityv (un) at that point are of the substantially same magnitude at the normal angular speed oi' maximal emciency (mmm), a chamber connecting the outlet oi' the secondary wheel with the inlet of the pump wheel, guide means operable in said chamber and consisting oi two rims one oi' which carries guide blades continually operative while the other rim carries supplementary blades for s low angular speeds of the secondary wheel and `means for rendering the supplementary blades inoperative at higher angular speeds and the guide means being arranged on the side of the circuit opposite to the side o i the secondary wheel, and a bladeless channel provided between the outlet oi' the turbine wheel and the inlet oi the supplementary guide blades.

HERMANN r'frrmenn. 

